Endless belt assembly with improved insert coupling

ABSTRACT

AN IMPROVED CONTINUOUS BELT ASSEMBLY SUITABLE FOR USE IN HIGH VELOCITY, MODERATE-LOAD POWER TRANSMISSION APPLICATIONS COMPRISING, IN COMBINATION, A NOVEL INTERNAL COUPLING MEANS AND A TOUGH EXTENSIBLE, FLEXIBLE AND TEAR RESISTANT POLYMERIC BELTING. THE COUPLING MEANS INCLUDES A CYLINDRICAL SHANK WITH A CONTINUOUS, CIRCULAR, EXTERNAL RIB HAVING AN OUTER HOLDING EDGE, PROXIMATE EACH OPPOSITE END THEREOF, SUCH EDGES BEING ADAPTED TO CUT INTO AND GRIP THE INTERIOR WALLS OF THE BELTING WHEN THE COUPLING MEANS IS INSERTED INTO HOLLOW ENDS OF THE BELTING AND THE BELTING IS SUBSEQUENTLY MOUNTED ON MACHINERY. WHEN MADE OF RIGID MATERIAL, THE SHARP EDGES ARE JOINED BY A CONNECTOR SHANK, OR SHAFT OF AT LEAST ABOUT 20% LARGER THAN THE INSIDE DIAMETER OF THE HOLLOW TUBULAR BELTING, THUS PROVIDING MEANS FOR MAINTAINING THE OUTER DIAMETER OF THE ELASTOMERIC BELT UNIFORM BETWEEN THE POINTS AT WHICH THE AFORESAID SHARP EDGES CUT INTO THE BELT. WHEN MADE OF FLEXIBLE MATERIAL, THE DIAMETER OF THE CONNECTOR SHANK OR SHAFT MAY BE EQUAL TO THE INSIDE DIAMETER OF THE TUBING.

P 20, 1971 A. G. PETERSON 3,605,201

ENDLESS BELT ASSEMBLY WITH IMPROVED INSERT COUPLING Original Filed March 25, 1968 73am JM ATTORNEYS United States Patent Office U.S. Cl. 24-31C 9 Claims ABSTRACT OF THE DISCLOSURE An improved continuous belt assembly suitable for use in high velocity, moderate-load power transmission applications comprising, in combination, a novel internal coupling means and a tough extensible, flexible and tear resistant polymeric belting. The coupling means includes a cylindrical shank with a continuous, circular, external rib having an outer holding edge, proximate each opposite end thereof, such edges being adapted to cut into and grip the interior walls of the belting when the coupling means is inserted into hollow ends of the belting and the belting is subsequently mounted on machinery. When made of rigid material, the sharp edges are joined by a connector shank, or shaft of at least about 20% larger than the inside diameter of the hollow tubular belting, thus providing means for maintaining the outer diameter of the elastomeric belt uniform between the points at which the aforesaid sharp edges cut into the belt. When made of flexible material, the diameter of the connector shank or shaft may be equal to the inside diameter of the tubing.

This application is a division of Ser. No. 715,869 filed Mar. 25, 1968 and now Pat. No. 3,501,971.

BACKGROUND OF THE INVENTION This invention relates to power transmission means and, more particularly, to a novel endless belt assembly having a novel fastening means and a polymeric belt component of selected physical properties.

The advent of extruded lengths of polymeric materials has been accompanied by efforts to adapt such materials to endless belt applications. A number of fastening means were available for the purpose of connecting two free ends of belting together to form a continuous length. For example, fasteners such as hose couplings could be used, but were impractical for having flanges, barbs, etc., which damaged the belting. Moreover, since many of the endless belt materials were meltable, melt-fusion techniques were also used to form continuous belts. Such methods as these, however, left much to be desired; they normally require special equipment and techniques and are difiicult to apply on equipment where there is little room to work and where the belt must be formed in situ.

Other types of sharp pointed prong or barb connector devices tended to tear unreinforced polymeric belting material within an undesirably short time under only moderately severe service conditions.

A major improvement in such fastening means is disclosed in the commonly-owned and co-pending applica tion, Ser. No. 651,527 filed on July 6, 1967, by Arnold G. Peterson. In that application, a novel fastening means in combination with a tough elastomeric tubing was disclosed. While this was a great improvement over the art and received widespread commercial acceptance, it was found that, in very severe service, the plurality of sharp edges did tend to tear the belt and the connector shaft linking the two holding heads sometimes broke under strain. These problems were in part due to the configuration of the elastomeric tubing over the cutting head, a

3,605,201 Patented Sept. 20, 1971 configuration resulting in successive bumps from the coupling at both extremities of the fastening means as the belt travelled around a pulley. It is believed that these bumps increased the vibrations to which the assembly was subjected during use and, consequently, contributed to its failure in very severe service.

Thus it is a principal object of the present invention to provide a power transmission means which consists of an easily connected endless belt useful under high loads and high velocities for long periods of time without excessive deterioration or tearing of the belt.

It is a further object of the invention to provide an endless belt assembly which can be quickly mounted in a minimum of time and space in situ on a machine without the use of tools.

Another object of the invention is to provide an endless belt assembly with good frictional characteristics for power transmission applications.

Another object of the invention is to provide a novel fastening means for use in the endless belt assembly of the invention.

SUMMARY OF THE INVENTION Applicants have achieved these objects by utilizing a belting, hollowed at least at the terminals thereof, which belting is comprised of a tough, tear-resistant, and elastic polymer having good abrasion resistance and excellent frictional characteristics for transmitting power between even rather smooth pulley surfaces, together with a coupling means having continuous, circular, external ribs with sharp edges as gripping heads, the sharp edges being adapted for cutting and gripping, but not tearing the aforesaid polymeric belting, and either a relatively short connector shaft having a diameter of at least about 20% greater than the inside dimension of the belting when made of metal, or a relatively long connector shaft, equal in diameter to the said inside dimension when made of flexible material.

The criticality and function of various attributes advantageously possessed by the polymer for co-action with the novel coupling means are discussed hereinbelow.

Toughness and tear resistance These characteristics allow the polymeric belting to withstand any cutting action of the coupling means and, further, to withstand the tension on the points, resulting from the predetermined deformation of the belt without progressive tearing of the belting.

Elasticity The polymeric belting in order to be most easily fitted onto some types of equipment must be stretchable at tensions reasonably exertable by a workman. Moreover, the material must then snap back so that it will fit snugly over the pulleys for eflicient power transmission.

Abrasion resistance Belting in high-speed friction-transfer, power transmission applications is subjected to frictional wear. A belting selected for the practice of the instant invention ran successfully for three times as long as the worn belting which it replaced in a typical application. Furthermore at the end of this time, there was no sign of deterioration.

In general, belting used in the instant invention should be constructed of a belting having the following characeristics.

Tear strength; Die B, nicked-at least about 200 lbs. per inch.

Tensile strength elongation The belting should be sufficiently easy to elongate so that an ordinary workman can extend the length of the 3 belt by at least about 4% to A belt of the invention, therefore, should require no more than about ten pounds force to elongate it to about 4%; preferably not more than about 100 psi. at temperatures of about 25 C. These latter values are based on an assumption that the belting has a cross-sectional area approximately the same as that of the illustrative example of this invention.

One polymer that ideally suits these requirements is a thermoplastic polyurethane such as that sold under the trade designation MPl485 by Molded Products Division of the Easthampton Rubber Thread Company.

The coupling means can be machined from aluminum or nylon, by means of an automatic screw machine, or may be injection-molded or otherwise formed. When formed of a flexible material, it is preferred to use a polyurethane elastomer of a grade employing the casting system or a thermo processable grade using a compression or injection molding system. One grade found suitable is an injection molding grade sold by Mobay Chemical Company under the name Texin urethane 355D and another suitable grade is a blend of Texin 480A and Texin 355D.

In the drawing:

FIG. 1 is a side elevation, in section, of a fragment of a belt passing around a pulley and connected by a coupling means of the invention.

FIG. 2 is an enlarged view of the coupling means of FIG. 1, in half section.

FIG. 3 is an end view thereof.

FIG. 4 is a view similar to FIG. 1 showing a flexible coupling means of the invention, in a belt, and passing around a pulley.

FIG. 5 is an enlarged fragmentary side elevation, in half section, of a V belt having a hollow cavity for receiving a coupling.

FIG. 6 is a view similar to FIG. 4 of another embodiment of the invention, and

FIG. 7 is an enlarged fragmentary side elevation, in half section, of the coupling insert shown in FIG. 6.

As shown in the drawing, designates a hollow, tubular elastomeric belt having an exterior normally cylindrical face 21 of predetermined outside diameter, an interior normally cylindrical face 22 of predetermined inside diameter, and the interior space 23. Belt 20 may be cut to any desired length so that the opposite free ends 24 and 25 may be joined to form an endless closed loop. It will be apparent that tubing of solid cross section could be used in the device of the invention, with a suitable cavity at each opposite end, but that hollow tubing is more practical and readily adapted to cutting into desired length.

The coupling means 27 is unitary and symmetrical, being formed of one piece of suitable material such as a tough plastic, metal or the like. It comprises the cylindrical connector shank or shaft 28, which, when made of rigid material (FIGS. 13) is of a diameter of at least about 20% greater than the inside diameter of the interior face 22 of belt tubing 20, and a pair of identical integral heads 29 and 30. Each head, such as 30, includes an external, continuous, circular rib, ridge, or flange 31, having a sharp outer gripping edge 32. Edge 32 is formed of a bearing face 33 and a truncated conical face 34. Bearing face 33 is normal to the axis of shank 28 and face 34 forms a 45-degree angle with bearing face 33. Moreover, each head, 29 and 30, includes an end face 35 having a bevel face 36 forming means 37 to promote insertion of heads 29 and 30 into belt tubing 20. Means 37, of course, could alternately be formed by any form of sloping surface, e.g. a rounded face as in FIG. 4.

In the embodiment of the invention illustrated in FIGS. 1-3, the inside diameter D of tubing 20 is 0.07 inch and the outside diameter of tubing 20 is .17 inch. Shank 28 has a diameter B of 0.091 inch, i.e. 30% larger than the inside diameter of tubing 20. Gripping edge 32 has a diameter A of 0.127 inch, i.e. about 40% larger than the diameter of shank 28. The length C between the sharp external circular edges 32 of heads 29 and 30 is critical in that when coupling means 27 is of rigid material, such as metal, length C is relatively short, but when coupling means 27 is of flexible material, length C is relatively lon 'I hus the structure and dimensions of the insert coupling 27 are such that the free ends 24 and 25 of the tube are maintained in a round configuration of substantially the same diameter in the area 42 at which the two free ends are joined, i.e. the space between gripping edges 32 on each of gripping heads 29 and 30.

The angle 38 formed by faces 33 and 34 may be deviated from to some extent, but when a single rib at each end is used, the bearing face 33, which is adapted for bearing the force exerted by tubing 20 on coupling means 27, should be substantially vertical.

However, as shown in FIG. 4, a one-piece, coupling means 40, when made of flexible material such as polyurethane elastomer, may have truncated conical faces 41 and 42 in lieu of vertical bearing faces 33 on the ribs 31, provided there are a second pair of similar ribs, such as 43 and 44. Thus four sharp, continuous outer gripping edges 45 are provided to firmly anchor the flexible insert in the tube 20.

The shank 46 of flexible insert 40 is of a diameter D equal to the inside diameter of tube 20, and as in the case of coupling 27, the cylindrical surface 47 of the shank 46 is smooth and free of barbs, flanges, or other obstructions.

As shown in FIG. 5, an endless belt 50 of V cross section may be connected by the coupling means of the invention inserted in a suitable hollow space or cavity 23 therein, to take the place of the well known size #40 open end V belt which is connected by staples at the joint.

As shown in FIG. 6, another embodiment 52 of the coupling means 27 is of flexible material, such as nylon, polyurethane or the like, and, as in the case of the flexible insert 40, is of relatively greater length C than the length C of the rigid coupling means 27 to permit flexing as the belt 20 passes around the sheave 53. Coupling means 52 has only a single pair of external ribs 54 and 55, each with an outer, sharp, continuous circular gripping edge 56, corresponding to edges 32, the bearing faces 57 and 58 being normal to the axis of the flexible, smooth shank 59, to correspond with the bearing faces 33. The truncated conical faces, 61 and 62, are preferably at an angle of about 30 to the shank axis and are continuous from the edge 56 to the terminal tip 63 of each head. As shown in dotted lines at '64, the coupling 52 may be hollow to increase the flexibility of the insert and it will be obvious that the coupling 40 may also be hollow for flexibility, if desired.

The relatively short shank 28 (length C) of the rigid insert means 27 is for the purpose of reducing the tendency illustrated in FIG. 1, of the rigid insert to continue in its straight line path at the leading end, when rounding the curved path of the pulley 53, while the belt 20 seeks to flex into the curved path the shorter shank 28 shortens the ridged section of the belt joint and therefore reduces any whip, bump, or fracture effect. At velocities of 4000 rpm. and higher and/or with pulleys of 1 /8" diameter, or smaller, rigid metal couplings such as 27, tend to create fatigue directly in advance, or in rear, of the coupling insert, caused by the bi-axial stretch on the belt by the insert and the inability of the belt to flex and follow its natural path due to the rigid, ribbed insert.

By forming the insert of flexible, tough plastic, a reliable, long-lasting joint is provided at the higher speeds. As shown in FIG. 4 and FIG. 6, the ends, 24 and 25,, of the belt are able to form a slight gap 65 in rounding the curved path, the gap 65 closing along the straight stretch of the belt. The 30 angle of the flexible circular insert 40 (FIG. 7) has been found to permit easier insertion while giving more support to the sharp gripping edges 56 of the heads. The resistance to flexing of the flexible inserts 40 and 52 is proportional to the thickness in cross section of the shank. The hollow 64 permits flexibility for small diamreduced diameter, to facilitate insertion thereof in an end of a belt;

and a pair of annular, outwardly projecting integral ribs each spaced from the adjacent tip and spaced apart from each other to define a central shaft thereetersheaves while providing good stitfnessandanchoring between; effect to the circular, continuous edges 56 and 45. said shaft having a cylindrical surface of predetermined As shown in the table set out below, while the flexible length extending between said ribs and being of inserts-of the invention may have a shank diameter B predetermined diameter less than the diameter of equal to the inside diameter of the belt 20, a greater disaid ribs to withstand high veloc ties and loads to ameter of the shank is preferred. which an endless belt may be sub ected;

' Insert dimensions Min. Belt dimensions pulley Belt Dia. Dia. Length Max. dia, size I.D. 0.1). Wall A B C Conditions r.p.m. in.

' 10M 1 Special. 070 170 050 115 080 :238 }May be used with flexible insert or iigid insert g /I .187 .055 .135 .090 .250 Rigid insert recommended "E y/I .250 .074 .155 .115 .250 2 .312 .092 .190 .140 .312 4M 1% .375 .111 .215 .170 .375 Minimum pulley diameter preferably about eight times the belt 4M 13/ .437 .120 .245 .105 .437 diameter. 4 1% .500 .147 .300 .230 .500 M 1% The 30, or more, slope of the heads of the insert, plus the enlarged diameter of the shank, while tending to make insertion into the tube more difficult, are responsible for the unusual tenacity with which the insert anchors the belt during use because of the increased friction, the internal pressure of the smaller diameter, stretched belt and the consequent penetration embedment, or distortion of the belt by the edges 32.

The belt and coupling of the invention are especially for use on a typical textile spinning frame of the type in which perhaps one hundred spindles on each side are each driven by an individual belt. It is usually impossible to replace a closed one-piece loop belt in such a machine because of other parts and inability to adjust length. The belt of this invention is easily cut to the correct length, trained on the pulleys and joined by. an insert 27, 40, or 52 at the free ends by manually pressing the insert into position. Typically, the belt will operate under a tension of about ten pounds and at about three thousand r.p.m., but will withstand considerably greater tension without separating at the joint.

The continuous, circular edge configuration of the gripping heads of the insert coupling of the invention has been found to avoid cutting into the material of the tube under light load conditions of up to about three pounds. Under loads of three pounds, or more, the sharp, circular edges may distort and embed or partially cut and penetrate into the material. Any penetration is significant but does not result in excessive tearing of the belting because of the shape of the gripping heads and the toughness of the elastomeric polymer.

The particular belt illustrated is designed to run at the maximum of 4000 rpm, a running load of five pounds and twenty pounds starting torque at the point of connection. The sharp circular edges may indent and cut into the tube wall, under these conditions, but will not continue to cut or tear, as would a plow cutting a furrow, because of the flat bearing faces of the heads or because of the multiple ribs.

What is claimed is:

1. A one-piece coupling insert for joining the opposite ends of an endless belt of polymeric material to form a closed loop;

said insert comprising an elongated one piece body adapted to be inserted within the opposite ends of an endless polymeric belt;

a terminal tip at each opposite end of said body, of

each said rib having a truncated conical surface inclined outwardly and rearwardly at an angle of at least and terminating in a continuous, circular, sharp, exterior edge for embedment, and cutting, into said belt, to anchor the same.

2. An insert as specified in claim 1 wherein:

each said rib includes a second truncated, conical surface inclined outwardly and forwardly at an angle of at least 30 and terminating in said circular sharp exterior edge.

3. An insert as specified in claim 2 plus a second pair of said ribs, each spaced inwardly from a rib of said first mentioned pair to provide a plu rality of said cutting edges at each end of said insert.

4. An insert as specified in claim 1 wherein:

said one piece body is solid and formed of metal.

5. Aninsert as specified in claim 1, wherein said one piece body is formed of a tough, elastic, tear resistant, flexible polymeric material.

6. An insert as specified in claim 5, wherein said one piece body is a hollow tube.

7. As an improved article of manufacture,

a one piece coupling for joining the opposite ends of a tubular belt, said coupling comprising:

an elongated cylinder of tough, flexible, polymeric material having a smooth, unobstructed, circumferential face of uniform diameter, and having terminal ends of reduced diameter,

a pair of integral, spaced apart, ribs, proximate each end of said cylinder, each rib being of triangular section terminating in an outer sharp edge at the apex thereof;

the diameter of said circumferential face of said cylinder being at least 20% greater than the inside diameter of the belt with which said coupling is to be used.

8. A one-piece coupling insert for joining the opposite 65 ends of a flexible, resilient, relatively light weight, endless belt to form a closed loop;

said insert having an elongated, cylindrical, central shank of uniform predetermined diameter and having a circumferential surface of predetermined length; and a pair of annular, outwardly projecting integral ribs each proximate an opposite end of said shank and spaced apart from the other to define the said cylindrical surface of said central shank therebetween; each said rib having a truncated conical surface inclined 7 outwardly and rearwardly at an angle of at least 30 and terminating in a continuous, circular, sharp, exterior edge for embedment, and cutting into said belt, to anchor the same,

the diameter of said circular continuous edge being greater than the diameter of the said cylindrical surface of said shank.

9. As an improved article of manufacture,

a one piece coupling for joining the opposite ends of a tubular belt, said coupling comprising:

an elongated cylinder having a smooth, unobstructed,

circumferential face of uniform diameter, and having terminal ends;

a pair of integral, spaced apart, ribs, proximate each end of said cylinder, each rib being of triangular section terminating in an outer sharp edge at the apex thereof;

the diameter of said circumferential face of said cylinder being at least 20% greater than the inside diameter of the belt with which said coupling is to be used.

References Cited UNITED STATES PATENTS 311,883 2/1885 England 24.--123RC 2,630,857 3/1953 Cohen 287-126X 2,896,285 7/1959 Morin 24-90RP 3,254,443 6/ 1966 Olson 46220 FOREIGN PATENTS 90,502 2/1961 Denmark 2431.2

OTHER REFERENCES 1,170,887, German printed application, May 1964,

W.R.P., 287-2.

15 DONALD A. GRIFFIN, Primary Examiner US. Cl. X.R. 

